EP1900973B1 - Hydraulisches Frakturierungsverfahren und Frakturierungspumpenvorrichtung - Google Patents

Hydraulisches Frakturierungsverfahren und Frakturierungspumpenvorrichtung Download PDF

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Publication number
EP1900973B1
EP1900973B1 EP06291449A EP06291449A EP1900973B1 EP 1900973 B1 EP1900973 B1 EP 1900973B1 EP 06291449 A EP06291449 A EP 06291449A EP 06291449 A EP06291449 A EP 06291449A EP 1900973 B1 EP1900973 B1 EP 1900973B1
Authority
EP
European Patent Office
Prior art keywords
drive
gear
pump
prime mover
input drive
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Not-in-force
Application number
EP06291449A
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English (en)
French (fr)
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EP1900973A1 (de
Inventor
André Salvaire
James Metson
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Services Petroliers Schlumberger SA
Gemalto Terminals Ltd
Prad Research and Development NV
Schlumberger Technology BV
Schlumberger Holdings Ltd
Original Assignee
Services Petroliers Schlumberger SA
Gemalto Terminals Ltd
Prad Research and Development NV
Schlumberger Technology BV
Schlumberger Holdings Ltd
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Services Petroliers Schlumberger SA, Gemalto Terminals Ltd, Prad Research and Development NV, Schlumberger Technology BV, Schlumberger Holdings Ltd filed Critical Services Petroliers Schlumberger SA
Priority to DE602006015054T priority Critical patent/DE602006015054D1/de
Priority to AT06291449T priority patent/ATE472040T1/de
Priority to EP06291449A priority patent/EP1900973B1/de
Priority to SG200706292-0A priority patent/SG141327A1/en
Priority to US11/849,470 priority patent/US7901314B2/en
Priority to EA200701720A priority patent/EA011575B1/ru
Priority to CN200710164877.4A priority patent/CN101255907B/zh
Publication of EP1900973A1 publication Critical patent/EP1900973A1/de
Application granted granted Critical
Publication of EP1900973B1 publication Critical patent/EP1900973B1/de
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B9/00—Piston machines or pumps characterised by the driving or driven means to or from their working members
    • F04B9/02—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being mechanical
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B17/00—Pumps characterised by combination with, or adaptation to, specific driving engines or motors
    • F04B17/05—Pumps characterised by combination with, or adaptation to, specific driving engines or motors driven by internal-combustion engines
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H47/00—Combinations of mechanical gearing with fluid clutches or fluid gearing
    • F16H47/02—Combinations of mechanical gearing with fluid clutches or fluid gearing the fluid gearing being of the volumetric type
    • F16H47/04—Combinations of mechanical gearing with fluid clutches or fluid gearing the fluid gearing being of the volumetric type the mechanical gearing being of the type with members having orbital motion
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H37/00—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00
    • F16H37/02—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings
    • F16H37/06—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts
    • F16H37/08—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing
    • F16H37/0833—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing with arrangements for dividing torque between two or more intermediate shafts, i.e. with two or more internal power paths
    • F16H37/084—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing with arrangements for dividing torque between two or more intermediate shafts, i.e. with two or more internal power paths at least one power path being a continuously variable transmission, i.e. CVT
    • F16H2037/088—Power split variators with summing differentials, with the input of the CVT connected or connectable to the input shaft

Definitions

  • the present invention relates to transmission systems for taking drive from a prime mover to an operating unit.
  • the invention related to such a transmission for use in driving pump, especially pumps of the type used in the oil and gas exploration and production industries for fracturing and cementing operations.
  • fracturing pump setup In a typical fracturing pump setup, several pumps are used, each typically being fitted with a diesel engine as primary driver for a high pressure triplex or quintuplex positive displacement pump, coupled through a five to seven speed transmission. Each pump typically delivers between 1500 to 2000 HP depending on the type and size of the engine fitted. Large fracturing operations can require more than 16 pumping units to be available at the well site to meet the pumping power requirements and provide backup in case of failure of individual units.
  • a stand-by unit In the event that an active pump fails during the operation, a stand-by unit is required to take its place. In this case the stand-by pump will need to start against a high pressure from standstill. In order to do this, operators must put the engine at speed and engage the desired gear.
  • the transmissions typically used are fitted with a torque converter that allows a limited amount of slip between engine speed and pump speed. However the unit will only tolerate running with such internal slippage for a very limited amount of time.
  • HST hydrostatic transmission
  • Such systems provide a gearless drive mechanism that translates engine power to hydraulic power continuously.
  • Such systems are widely applied in construction machinery, because of their superior speed changeability.
  • HST does have certain problems that make is unsuitable for pumping systems, e.g. limited low speed / torque range and narrow shift range.
  • HST is one form of a continuously variable transmission (CVT).
  • CVT continuously variable transmission
  • a CVT avoids some of the problems of changing gears in a conventional automatic gear box by allowing any ratio of input and output to be obtained.
  • Mechanical CVTs are well known in automotive applications.
  • An extension to CVT design allows the transmission to drive a vehicle backwards as well as forwards.
  • Transmission input is split into two shafts with one connected to an epicyclic gear set and the other to a CVT.
  • the output from the CVT is connected to a different set of gears in the epicyclic.
  • the gear that does not draw power from engine or CVT transfers torque to the transmission output.
  • the epicyclic gear set acts as a mechanical adding machine to subtract or add one speed from the other.
  • Hybrid automobiles also use epicylic gear system to allow both power sources to be connected to the vehicle transmission.
  • US4311066 describes the use of an epicyclic gear system in a dredge pump, to allow steady speed adjustments in dredge pump drive systems.
  • An object of this invention is to provide a transmission system that has the advantages of a CVT in a form that can be used effectively in a pump drive system. This object is achieved in the invention by the use of a epicylic gear system.
  • One aspect of the invention comprises a method of performing a hydraulic fracturing operation in an oil or gas well comprising:
  • the epicylic gear system acts to mechanically add or subtract the two drives and so provide any input:output ratio according to the speed and direction of each drive. Changes to the ratio can be made without any harsh physical shocks on either the transmission system, prime mover or pump.
  • the planet gear typically comprises a number of gears mounted on a carrier, the hydraulic auxiliary input drive or the output drive being connected to the carrier.
  • the hydraulic auxiliary input drive can operate in forward or reverse directions.
  • Another aspect of the invention comprises a fracturing pump system for use in oil or gas well operations comprising a prime mover arranged to drive a pump via a transmission system according to the previous aspect of the invention.
  • the main and hydraulic auxiliary input drives can be mechanical or hydraulic.
  • a torque converter is provided between the prime mover and the transmission system.
  • the pump is preferably a pump such as a triplex or quintuplex pump for use in fracturing, cementing or coil tubing operations in oil wells.
  • Figure 1 shows a schematic of a transmission system according to an embodiment of the invention
  • Figures 2-5 show schematic views of various embodiments of the invention.
  • the invention is aimed at providing smooth power and/or torque transfer between a prime mover (e.g. diesel engine, electric motor) and the pump, allowing the assembly to have full power and /or torque available irrespective of the speed.
  • a prime mover e.g. diesel engine, electric motor
  • the basic structure of a system according to the invention based on a single split input that uses an epicylic gear train as differential mechanism, one differential output being used to drive the pump and the second differential output being connected to a speed regulating mechanism (the auxiliary drive) such that this second output is in effect an input and the differential acts to combine the two inputs rather than to split a single input into two outputs.
  • the main input drive diesel engine or electric motor
  • the main input drive can be allowed to run at constant speed at the maximum torque speed and drive the pump from 0 rpm to maximum without the need of step gears. This allows the unit to start from standstill and gradually increase the pump speed to the desired operation speed without any slippage or gear changes and maintaining the primary drive at a constant speed.
  • a suitable epicylic gear train mechanism consists of a sun gear, a planetary gear, a ring gear and two or more carriers that constrain the planetary gear.
  • the epicylic gear system is used as reduction or step gear.
  • input or output is given at this constraint point.
  • the differential gear is made by splitting or combining input and output.
  • Figure 1 shows a schematic of a transmission system according to an embodiment of the invention for use in driving a fracturing pump in an oil well stimulation operation.
  • Drive from the prime mover D diesel engine
  • Drive is also lead from the prime mover D to the input end 12 of an auxiliary drive system A via suitable connection 14.
  • the auxiliary drive A in the embodiment of Figure 1 is an HST (hydraulic pump/motor), the input drive 12 from the prime mover D being used to drive the HST pump 16 which in turn is used to drive the HST motor 18 in the usual manner.
  • the output end of the auxiliary drive A is provided with a drive connection 20 which is in turn lead to the ring gear 22 of the epicyclic transmission system.
  • the output shaft 24 is connected to the carrier 26 of the planet gear 28 in the epicylic transmission system.
  • the output shaft is connected to the fracturing pump P.
  • the auxiliary drive A is acting as a continuously variable input to the epicylic differential.
  • a part of the output from the prime mover can be applied to the ring gear of the transmission system to determine the final drive ratio applied to the pump P.
  • speed control of the output shaft 24 is effected by controlling the speed and direction of the auxiliary drive A while the prime mover speed can remain effectively constant.
  • Figure 2 shows schematically the arrangement of Figure 1 in which the prime mover D is connected to the sun gear 10, the auxiliary drive A (in this case constituted by HST H1 which is powered from the prime mover D) is connected to the ring gear 22 and the pump shaft P is connected to the planet gear carrier 26.
  • Figure 3 shows a variation of this embodiment wherein the drive to the sun gear 10 is provided by a further HST H2, also powered by the prime mover (not shown).
  • Figure 4 shows a different configuration in which the prime mover D is connected to the sun gear 10, the auxiliary drive A (constituted by HST H1 which is powered from the prime mover D) is connected to the planet gear carrier 26 and the pump shaft P is connected to the ring gear 22.
  • Figure 5 shows the corresponding arrangement with two HSTs (HST1 and HST2) in pace of the arrangement of the prime mover D and auxiliary HST1 of Figure 4 (cf Figure 3 ).
  • HST of the auxiliary (or main) drive can be replaced by another form of CVT.
  • One particularly preferred variation is to provide a torque converter at the prime mover end to improve its characteristics on start-up and shutdown and during major changes of speed and torque delivery.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Structure Of Transmissions (AREA)
  • Details And Applications Of Rotary Liquid Pumps (AREA)
  • Rotary Pumps (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Other Liquid Machine Or Engine Such As Wave Power Use (AREA)
  • Supply Devices, Intensifiers, Converters, And Telemotors (AREA)

Claims (8)

  1. Verfahren zum Ausführen einer hydraulischen Zerklüftungsoperation in einem Öl- oder Gasbohrloch, das umfasst:
    - Vorsehen mehrerer Pumpeneinheiten, wobei jede Einheit ein Zerklüftungspumpensystem enthält;
    - Betreiben der Zerklüftungspumpensysteme, um Fluid im Bohrloch nach unten zu liefern, wobei wenigstens ein Zerklüftungspumpensystem eine Antriebsmaschine (D) enthält, die dazu ausgelegt ist, eine Zerklüftungspumpe (P) über ein Getriebesystem anzutreiben, wobei das Getriebesystem umfasst:
    - ein Planetengetriebesystem, das ein Sonnenrad (10) und ein Hohlrad (22) sowie ein Planetenrad (28), das zwischen dem Sonnenrad (10) und dem Hohlrad (22) in Eingriff ist, enthält;
    - einen Haupteingangsantrieb, der dazu ausgelegt ist, durch die Antriebsmaschine (D) angetrieben zu werden;
    - einen hydraulischen Hilfseingangsantrieb (A), der dazu ausgelegt ist, durch die Antriebsmaschine (D) angetrieben zu werden; und
    - einen Ausgangsantrieb (24), der dazu ausgelegt ist, die Pumpe (P) anzutreiben;
    wobei der Haupteingangsantrieb mit dem Sonnenrad (10) verbunden ist und wobei entweder
    (i) der hydraulische Hilfseingangsantrieb (A) mit dem Hohlrad (22) verbunden ist und der Ausgangsantrieb (24) von dem Planetenrad (28) wegführt; oder
    (ii) der hydraulische Hilfseingangsantrieb (A) mit dem Planetenrad (28) verbunden ist und der Ausgangsantrieb (24) von dem Hohlrad (22) wegführt.
  2. Verfahren nach Anspruch 1, wobei das Planetenrad (28) mehrere an einem Träger montierte Zahnräder umfasst, wobei der hydraulische Hilfseingangsantrieb (A) oder der Ausgangsantrieb (24) mit dem Träger verbunden ist.
  3. Verfahren nach Anspruch 1 oder 2, wobei der hydraulische Hilfseingangsantrieb (A) in Vorwärts- oder in Rückwärtsrichtung arbeiten kann.
  4. Verfahren nach einem der Ansprüche 1, 2 oder 3, wobei der Haupteingangsantrieb mechanisch oder hydraulisch ist.
  5. Verfahren nach einem der Ansprüche 1 bis 4, wobei das Pumpensystem ferner einen Drehmomentwandler umfasst, der zwischen der Antriebsmaschine und dem Getriebesystem vorgesehen ist.
  6. Verfahren nach einem der Ansprüche 1 bis 5, wobei die Pumpe eine Dreifach- oder Fünffachpumpe ist.
  7. Zerklüftungspumpensystem für die Verwendung in Öl- oder Gasbohrlochoperationen, das eine Antriebsmaschine (D) umfasst, die dazu ausgelegt ist, über ein Getriebesystem eine Pumpe anzutreiben; wobei das Getriebesystem umfasst:
    - ein Planetengetriebesystem, das ein Sonnenrad (10) und ein Hohlrad (22) sowie ein Planetenrad (28), das zwischen dem Sonnenrad (10) und dem Hohlrad (22) in Eingriff ist, enthält;
    - einen Haupteingangsantrieb, der dazu ausgelegt ist, durch die Antriebsmaschine (D) angetrieben zu werden;
    - einen hydraulischen Hilfseingangsantrieb (A), der dazu ausgelegt ist, durch die Antriebsmaschine (D) angetrieben zu werden; und
    - einen Ausgangsantrieb (24), der dazu ausgelegt ist, die Pumpe (P) anzutreiben;
    wobei der Haupteingangsantrieb mit dem Sonnenrad (10) verbunden ist und wobei entweder
    (i) der hydraulische Hilfseingangsantrieb (A) mit dem Hohlrad (22) verbunden ist und der Ausgangsantrieb (24) von dem Planetenrad (28) wegführt; oder
    (ii) der hydraulische Hilfseingangsantrieb (A) mit dem Planetenrad (28) verbunden ist und der Ausgangsantrieb (24) von dem Hohlrad (28) wegführt.
  8. Pumpensystem nach Anspruch 7, wobei die Pumpe eine Dreifach- oder Fünffachpumpe ist.
EP06291449A 2006-09-13 2006-09-13 Hydraulisches Frakturierungsverfahren und Frakturierungspumpenvorrichtung Not-in-force EP1900973B1 (de)

Priority Applications (7)

Application Number Priority Date Filing Date Title
DE602006015054T DE602006015054D1 (de) 2006-09-13 2006-09-13 Hydraulisches Frakturierungsverfahren und Frakturierungspumpenvorrichtung
AT06291449T ATE472040T1 (de) 2006-09-13 2006-09-13 Hydraulisches frakturierungsverfahren und frakturierungspumpenvorrichtung
EP06291449A EP1900973B1 (de) 2006-09-13 2006-09-13 Hydraulisches Frakturierungsverfahren und Frakturierungspumpenvorrichtung
SG200706292-0A SG141327A1 (en) 2006-09-13 2007-08-28 Transmission system for pump drive
US11/849,470 US7901314B2 (en) 2006-09-13 2007-09-04 Transmission system for pump drive
EA200701720A EA011575B1 (ru) 2006-09-13 2007-09-12 Трансмиссионная система для привода насоса
CN200710164877.4A CN101255907B (zh) 2006-09-13 2007-09-13 用于泵驱动的传动***

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP06291449A EP1900973B1 (de) 2006-09-13 2006-09-13 Hydraulisches Frakturierungsverfahren und Frakturierungspumpenvorrichtung

Publications (2)

Publication Number Publication Date
EP1900973A1 EP1900973A1 (de) 2008-03-19
EP1900973B1 true EP1900973B1 (de) 2010-06-23

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EP06291449A Not-in-force EP1900973B1 (de) 2006-09-13 2006-09-13 Hydraulisches Frakturierungsverfahren und Frakturierungspumpenvorrichtung

Country Status (7)

Country Link
US (1) US7901314B2 (de)
EP (1) EP1900973B1 (de)
CN (1) CN101255907B (de)
AT (1) ATE472040T1 (de)
DE (1) DE602006015054D1 (de)
EA (1) EA011575B1 (de)
SG (1) SG141327A1 (de)

Families Citing this family (62)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102004061034A1 (de) * 2004-12-18 2006-06-22 Daimlerchrysler Ag Verfahren zur Überwachung einer Getriebeölpumpe
WO2010144753A1 (en) * 2009-06-10 2010-12-16 Czero, Inc. Systems and methods for hybridization of a motor vehicle using hydraulic components
DE102009031382A1 (de) * 2009-07-01 2011-01-05 Robert Bosch Gmbh Antriebssystem und Verfahren zum Wechseln von Fahrbereichen des Antriebssystems
IT1395630B1 (it) 2009-09-10 2012-10-16 Gea Niro Soavi S P A Ora Gea Mechanical Equipment Italia S P A Omogeneizzatore ad alta pressione con riduttore epicicloidale
DE112012002888A5 (de) * 2011-07-08 2014-03-20 Ixetic Bad Homburg Gmbh Pumpenantrieb
US9085225B2 (en) * 2012-01-23 2015-07-21 Dennis Ray Halwes Infinitely variable transmission
WO2013148342A1 (en) * 2012-03-27 2013-10-03 Kevin Larson Hydraulic fracturing system and method
US20130306322A1 (en) 2012-05-21 2013-11-21 General Electric Company System and process for extracting oil and gas by hydraulic fracturing
US8997904B2 (en) * 2012-07-05 2015-04-07 General Electric Company System and method for powering a hydraulic pump
US10020711B2 (en) 2012-11-16 2018-07-10 U.S. Well Services, LLC System for fueling electric powered hydraulic fracturing equipment with multiple fuel sources
US10119381B2 (en) 2012-11-16 2018-11-06 U.S. Well Services, LLC System for reducing vibrations in a pressure pumping fleet
US10378335B2 (en) 2013-03-13 2019-08-13 Schlumberger Technology Corporation Pressure testing of well servicing systems
WO2014142833A1 (en) * 2013-03-13 2014-09-18 Schlumberger Canada Limited Pressure testing of well servicing systems
DE102013204747A1 (de) * 2013-03-19 2014-09-25 Zf Friedrichshafen Ag Getriebevorrichtung mit sekundär gekoppelter Leistungsverzweigung
CN103244620B (zh) * 2013-05-21 2014-07-02 江苏圣乐机械有限公司 机械换向减速器和立式抽油机
US9091267B2 (en) 2013-07-08 2015-07-28 Caterpillar Inc. Controller for varying flow rate from fixed displacement pump
US10655710B2 (en) 2013-12-31 2020-05-19 Deere & Company Multi-mode infinitely variable transmission that provides seamless shifting
US10670124B2 (en) 2013-12-31 2020-06-02 Deere & Company Multi-mode infinitely variable transmission
US10738868B2 (en) 2014-04-09 2020-08-11 Deere & Company Multi-mode powertrains
US9944163B2 (en) * 2014-04-09 2018-04-17 Deere & Company Multi-mode power trains
US10647193B2 (en) 2014-04-09 2020-05-12 Deere & Company Multi-mode power trains
DE102014211964A1 (de) * 2014-06-23 2015-12-24 Voith Patent Gmbh Pumpvorrichtung
US9638194B2 (en) 2015-01-02 2017-05-02 General Electric Company System and method for power management of pumping system
US10221856B2 (en) 2015-08-18 2019-03-05 Bj Services, Llc Pump system and method of starting pump
CN106608183A (zh) * 2015-10-27 2017-05-03 熵零股份有限公司 一种流体与机械混合驱动车辆
CN106609820A (zh) * 2015-10-27 2017-05-03 熵零股份有限公司 一种能量调整***
CN105240481A (zh) * 2015-11-18 2016-01-13 山东农业大学 一种大功率拖拉机液压机械无级变速器
RU2748925C2 (ru) 2016-01-19 2021-06-01 Твин Диск, Инк. Высокопроизводительная промышленная трансмиссия
DE102016212209A1 (de) * 2016-07-05 2018-01-11 Zf Friedrichshafen Ag Nebenabtriebsanordnung
CN106545637A (zh) * 2016-10-31 2017-03-29 广西柳工机械股份有限公司 动力分配调节***及装载机动力***
US10563649B2 (en) * 2017-04-06 2020-02-18 Caterpillar Inc. Hydraulic fracturing system and method for optimizing operation thereof
US10619711B2 (en) 2017-04-12 2020-04-14 Deere & Company Infinitely variable transmission with power reverser
US10415348B2 (en) * 2017-05-02 2019-09-17 Caterpillar Inc. Multi-rig hydraulic fracturing system and method for optimizing operation thereof
NO20171100A1 (en) * 2017-07-04 2019-01-07 Rsm Imagineering As A dual-acting pressure boosting liquid partition device, system, fleet and use
IT201700049551A1 (it) * 2017-07-10 2019-01-10 Luciano Valotto Meccanismo con volano di accumulo, per generatore di energia potenziale ad una o più stazioni, con idro-controllo della coppia.
CN108006188B (zh) * 2017-12-27 2020-06-26 北京理工大学 一种双速液压混合动力驱动***
CN108607181A (zh) * 2018-04-02 2018-10-02 江苏卡威专用汽车制造有限公司 一种消防车的驱动***
CN108374875A (zh) * 2018-04-25 2018-08-07 同济大学 一种变频变排量机械液压无级变速传动***
US11052747B2 (en) 2018-05-04 2021-07-06 Deere & Company Multi-mode powertrains
US11091018B2 (en) 2018-05-11 2021-08-17 Deere & Company Powertrain with variable vertical drop distance
RU185446U1 (ru) * 2018-08-20 2018-12-05 Общество с ограниченной ответственностью "КОМ" Коробка передач
US10914155B2 (en) 2018-10-09 2021-02-09 U.S. Well Services, LLC Electric powered hydraulic fracturing pump system with single electric powered multi-plunger pump fracturing trailers, filtration units, and slide out platform
CN109578544B (zh) * 2018-12-18 2021-04-27 河南科技大学 一种单行星排多模式液压机械无级变速器
US10975959B2 (en) 2019-04-01 2021-04-13 Deere & Company Transmission clutch braking control system
BR112021018247A2 (pt) 2019-04-17 2021-11-23 Twin Disc Inc Sistema de bombeamento eletro-hidráulico de alta pressão de campo de petróleo para acionar uma bomba de fraturamento, e, método para quebrar uma formação subterrânea usando um motor elétrico primário
CA3139970A1 (en) 2019-05-13 2020-11-19 U.S. Well Services, LLC Encoderless vector control for vfd in hydraulic fracturing applications
US11542786B2 (en) 2019-08-01 2023-01-03 U.S. Well Services, LLC High capacity power storage system for electric hydraulic fracturing
US11137052B2 (en) 2019-08-29 2021-10-05 Deere & Company Transmission assembly with integrated CVP
US11351983B2 (en) 2019-10-31 2022-06-07 Deere & Company Power control system with transmission transient boost function
JP7211928B2 (ja) * 2019-12-04 2023-01-24 株式会社クボタ 多目的車両
US11846085B2 (en) 2020-02-17 2023-12-19 Deere & Company Energy management system for a hybrid vehicle with an electrically powered hydraulic system
US11788395B2 (en) 2020-06-22 2023-10-17 Twin Disc, Inc. Oilfield pressure pumping system with slow speed and high pressure fracturing fluid output
US11754060B2 (en) 2020-09-01 2023-09-12 Fmc Technologies, Inc. Hydraulic fracturing pump system
US11325459B2 (en) 2020-10-09 2022-05-10 Deere & Company Low profile transmission assembly with integrated CVP
US11613246B2 (en) 2021-01-21 2023-03-28 Deere & Company Power control system with engine throttle shift function
CN112747090B (zh) * 2021-01-25 2023-04-14 重庆胜特佳机械有限公司 双动力多模无级变速耦合输出机构
US11628822B2 (en) 2021-02-09 2023-04-18 Deere & Company Power control system with stall prevention clutch modulation function
US11299141B1 (en) 2021-02-10 2022-04-12 Deere & Company System for multi-layer braking and retardation in a work vehicle
US11820361B2 (en) 2021-11-30 2023-11-21 Deere & Company Transmission assembly with electrical machine unit for improved shift quality
US11607948B1 (en) 2021-12-22 2023-03-21 Deere & Company Electronically-variable power shift transmission for work vehicles
US11585412B1 (en) 2021-12-22 2023-02-21 Deere & Company Electronically-variable, dual-path power shift transmission for work vehicles
US11913528B1 (en) 2022-10-28 2024-02-27 Deere & Company Multi-mode continuously variable transmission assembly with drop set arrangement

Family Cites Families (35)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB1062631A (en) * 1963-01-11 1967-03-22 Plessey Uk Ltd Improvements in or relating to composite hydromechanical constant-speed drives
US3383952A (en) * 1965-02-01 1968-05-21 Gen Motors Corp Hydrostatic-mechanical vehicle drive
US3534631A (en) * 1968-08-16 1970-10-20 Arthur B Keller Infinitely variable ratio constant mesh gearing system
US3665788A (en) * 1970-08-19 1972-05-30 Sundstrand Corp Hydromechanical storing transmission
US3714846A (en) * 1971-02-23 1973-02-06 Sundstrand Corp Hydrostatic-differential transmission
DE2460098C3 (de) * 1974-12-19 1982-06-16 Gewerkschaft Eisenhütte Westfalia, 4670 Lünen Elektrischer Kettenantrieb für Hobelanlagen, Kettenkratzförderer u.dgl.
GB1582430A (en) * 1976-12-22 1981-01-07 Secr Defence Variable ratio transmission systems
US4066123A (en) * 1976-12-23 1978-01-03 Standard Oil Company (Indiana) Hydraulic pumping unit with a variable speed triplex pump
DE2758660A1 (de) * 1977-12-29 1979-07-05 Zahnradfabrik Friedrichshafen Stufenlos regelbares getriebe mit leistungsverzweigung
DE2901560C2 (de) 1979-01-12 1980-09-25 Mannesmann Ag, 4000 Duesseldorf Untersetzungsgetriebe für eine Baggerpumpe
FR2482692B1 (fr) * 1980-05-14 1985-06-21 Renault Vehicules Ind Transmission a variation continue a deux modes de fonctionnement
CA1184789A (en) * 1981-02-21 1985-04-02 Julian Parraga Garcia Continuous, high-performance hydromechanical speed gear
JPS5846246A (ja) * 1981-09-16 1983-03-17 Ishikawajima Harima Heavy Ind Co Ltd 無段変速装置
US4489623A (en) 1982-05-03 1984-12-25 Caterpillar Tractor Co. Axle shaft and pump drive mechanism
US4774855A (en) * 1982-08-17 1988-10-04 Vickers Shipbuilding And Engineering Limited Apparatus for providing an electrical generator with a constant rotational speed from a variable speed input
SU1273670A1 (ru) * 1984-07-22 1986-11-30 Ленинградский Институт Водного Транспорта Гидромеханическа передача
US4721439A (en) * 1984-11-16 1988-01-26 Wiwa Wilhelm Wagner Gmbh & Co. Kg Piston pump and drive therefor
SU1272040A1 (ru) * 1984-12-24 1986-11-23 Предприятие П/Я Р-6194 Гидромеханическа передача
EP0235466B1 (de) * 1986-02-24 1990-06-27 Shimadzu Corporation Hydromechanisches Getriebe
SU1498940A1 (ru) * 1986-05-26 1989-08-07 Азербайджанский научно-исследовательский и проектно-конструкторский институт нефтяного машиностроения Шатунно-эксцентриковый привод многоплунжерного насоса
DE3812412A1 (de) * 1988-04-14 1989-10-26 Walter Schopf Pumpenantrieb fuer konstantpumpen im mobilantrieb
US5092824A (en) * 1990-10-09 1992-03-03 Connett Donald C Pump output control system with high efficiency hydromechanical variable speed drive
US5201691A (en) * 1990-11-07 1993-04-13 Doyle Transmissions Limited Variable speed transmission assembly
JP3343660B2 (ja) * 1992-12-10 2002-11-11 本田技研工業株式会社 オイルポンプ駆動装置
GB2322420B (en) * 1997-02-19 2000-12-27 Delphi France Automotive Sys Automatic transmission
AT500431B1 (de) * 1997-11-25 2006-11-15 Zahnradfabrik Friedrichshafen Hydrostatisch-mechanisches leistungsverzweigungsgetriebe mit grosser spreizung
DE10016435B4 (de) 2000-04-01 2014-03-13 Deere & Company Lüftungseinrichtung für ein landwirtschaftliches Fahrzeug
JP2001329948A (ja) 2000-05-23 2001-11-30 Nsk Ltd ポンプ駆動装置
RU2191303C2 (ru) * 2000-11-13 2002-10-20 Открытое акционерное общество "Курганмашзавод" Гидромеханическая трансмиссия
JP2002202083A (ja) * 2000-12-28 2002-07-19 Ishikawajima Harima Heavy Ind Co Ltd 羽根車可変速ポンプ
JP2002202084A (ja) * 2000-12-28 2002-07-19 Ishikawajima Harima Heavy Ind Co Ltd 羽根車可変速ポンプ
JP2005016476A (ja) * 2003-06-27 2005-01-20 Ebara Corp 立軸ポンプ
RU38828U1 (ru) * 2004-03-02 2004-07-10 Открытое акционерное общество "Строммашина" Установка насосная передвижная нефтепромысловая
US7252147B2 (en) * 2004-07-22 2007-08-07 Halliburton Energy Services, Inc. Cementing methods and systems for initiating fluid flow with reduced pumping pressure
US20090041588A1 (en) * 2007-08-08 2009-02-12 Halliburton Energy Services, Inc. Active valve system for positive displacement pump

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EP1900973A1 (de) 2008-03-19
DE602006015054D1 (de) 2010-08-05
EA200701720A1 (ru) 2008-04-28
CN101255907B (zh) 2013-10-02
ATE472040T1 (de) 2010-07-15
US7901314B2 (en) 2011-03-08
CN101255907A (zh) 2008-09-03
US20080182699A1 (en) 2008-07-31
EA011575B1 (ru) 2009-04-28
SG141327A1 (en) 2008-04-28

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